Telegraph printer



C. J. FITCH ETAL TELEGRAPH PRINTER Filed Nov. 18, 1941 July 6, 1943.

FIG.2.

5 Sheds-Sheet l July 6, 1943. c. J. FITCH ETAL TELEGRAPH PRINTER 5 Sheets-Sheet 2 Filed NOV. 18, 1941 3 wum a fl WA ATTORNEY July 6, 1943. c. .1. FITCH ETAL TELEGRAPH PRINTER Filed Nov. 18, 1941 5 She'ets-Sheet-S 6 l VENTO 5 5 2/;

ATTORNEY July 6, 1943. c. J. FITCH ETAL 2,323,338

TELEGRAPH PRINTER Filed Nov. 18, 1941 5 Sheets-Shae}, 4

' FIG. 6.

-' ATTORNEY Y 1943- c. J. FITCH ETAL 2,323,388

TELEGRAPH PRINTER 'Filed Nov. 18, 1941 5 Sheets-Sheet 5 A'TTORNEY Patented July 6, 1943 UNITED STATES PATENT OFFICE TELEGRAPH PRINTER Clyde J. Fitch, Endwell, and Kurt R. Schneider, Endicott, N. Y., assignors to International Business Machines Corporation, New York, N. Y., a corporation of New York Application November 18, 1941, Serial No. 419,577

, 4 Claims.

effectiveness of'such printing mechanism.

Other objects of the invention will be pointed out in the following description and'claims and illustrated in the accompanying drawings, which disclose, by way of example, the principle of the invention and the best mode, which has been contemplated, of applying that principle.

In the drawings:

Fig. 1 is a front elevational view, partly in section, illustrating the typewheel positioning mechanism.

Fig. 2 is a side elevational view, partly in section, illustrating the typewheel positioning mechanism and drive means therefor.

Fig. 3 is a top, plan view of the complete novel printer, including the tape feed mechanism.

Fig. 4 is a bottom, plan view, on an enlarged scale, of a portion of the novel printer.

Fig. 5 is a perspectiveview, on an enlarged scale, illustrating the details of the clutch mechanism utilized in positioning the typewheel.

Fig. 6 is a sectional view taken on line 6-6 of Fig. 4, and rotated 90 degrees counterclockwise.

Fig. 7 is a sectional fragmentary view, on an enlarged scale, taken on line l'l of Fig. 3.

Fig. 8 is a sectional fragmentary view, on an enlarged scale, taken on line 8-8 of Fig. 4.

Fig. 9 is an exploded view, on an enlarged scale, illustrating the details of the shift mechanism for rotatably shifting the typewhe'el.

prises a supporting frame 20 (Figs. 2, 3 and 4) including a front panel 20a, a side frame member 20b and protruding semicircular front portions 20c.

A motor 2! (Fig. 3) carried by the frame 20 drives shaft 22 carrying the worm 23 meshin with worm wheel 24 carried by shaft 25 (Fig. 2).

Shaft 25 is suitably journaled at each end in frame 29 and carries at one end thereof the fiber driving gear 26 (Figs. 1 and 2) for driving the mechanism controlling the rotative positioning of the typewheel. -At its other end, the shaft 25 carries the fiber driving gear 27 for driving the mechanism that axially positions the typewheel.

By the mechanism just described, motor 2i drives shaft 25 at 900 R. P. M., which is not synchronous speed but is faster than the speed of. the incoming signals.

Gear 25 meshes with gear 28 carrying a shaft 29 on which is mounted ratchet gear 30.

Gear 27! meshes with gear 3i carrying a shaft 32 on which is mounted ratchet gear 33.

Gears 3i! and 33 are thereby driven at 1200 R. P. M. Gear it drives the eight position clutch mechanism 35!, which in turn is controlled by permutation disk mechanism, all as described presently, to rotatably position shaft 35 and typewheel 36, while gear 33 drives the four position clutch mechanism 31, also controlled by permutation disk mechanism, to rotatably position the cylindrical cam member 38 which, as described later, by its rotative positioning controls the axial positioning of the typewheel.

Clutch 3B rotatably positions the typewheel 36 in any one of eight uniformly distributed rotative positions whereby any one of eight vertical columns of characters (Fig. 2) may be selectively positioned in printing position. Novel shift mechanism is also provided, as described later,

scale, illustrating the details of the adjusting and operating mechanism for. the printing hammer.

Referring to the drawings and more particu larly to Figs. 1, 2, 3 and 4, the novel printer comto further rotatably position the typewheel 35, in positions respectively intermediate each of these eight rotative positions, whereby the typewheel is selectively adjusted to alternate ones of two rotative positions corresponding to each of the above eight rotative positions.

Gear 21 (Fig. 2) also meshes with gear 39 carrying a shaft 40 on which is mounted ratchet gear M for driving the clutch 42, which clutch is controlled by single revolutionmechanism, described later, to permit rotation of shaft 43 under the control of clutch for one complete revolution only. Shaft 43 carries a plurality of cams, so distributed circumferentially of shaft 43 as to operate in proper time sequence, the ribbon feed,

tape feed, printing hammer cocking and release mechanism, restoring mechanism and shift mechanism of the novel printer, all as described in detail later. 7 i

Clutch mechanism The clutch devices 34,. 31 and 42 may be of the type, as fully/shown and described inPatent No. 2,206,646, granted to Kurt Rhschneider July 2, 1940.- Referring to Fig. 5, there is illustrated. therein the construction of such a clutch, which in the particular instance, may be rotatably posia,sas,aes

- for rotatably positioning the typewheel, means for axially positioning the typewheel and means for zone positioning or shifting the typewheel,

I which zone positioning comprises rotatively positloned in any one of, four different positions (such as clutch 310! Fig. 2) but it is to be un-,

derstood that the construction of each of the clutches 34, 31 and 42, respectively, is the same, with the sole exception of the number of rotative positions to be assumed by the clutch. As

illustrated in Fig. 5, the clutch comprises a cylindrical member 44 provided with a series of four notches 441i distributed about a flange member 44a integral with member 44. A shaft portion 44b, also integral with member 44, is provided,

member 44a to cooperate with a notch and thus prevent back'rotation of the clutch, when stopped in any one of its four positions. The

face 44! of member 44 of the four position clutch illustrated in Fig. 5, is located adjacent its cooperating ratchet gear 33 (see also Fig. 1) driven groups ofv characters; will be printed.

tioning jthe typewheel intermediate each of the eight [assumed rotative positions mentioned above, to determine which character out of two primary These sets of means will now be-described in de- Rotative positioning of the tzl'pewheel As illustrated in Figs. 3 and 4,, a plurality of live -permutatiorimagnets and also a printing magnet are provided. Each of the five permutation magnets is responsive to one element of a 5-unit code signal received. Three of-the magnets 59, ii and'52 (Fig. 3), controlled, respectively, by the first, second and fifth code signal elements, are utilized to control permutation disk or ring members which in turn regulate the rotative positioning of the typewheel. Two

of the magnets 53 and 55 (Fig. 4) controlled, respectively, by the third and fourth code signal elements are utilized to control the permutation ring members which in turn regulate the axial positioning of the typewheel. The print magnet 54 controls mechanism for regulating the-rotation of clutch 42 to produce a single revolutionv only, of clutch 42 and its associated T-shaft, which in turn controls the zone posif -tloning of the typewheel and also controls, in proper sequence, the tape and ribbon feed, the

print: hammer cooking and releasing functions by shaft 32, as described above. A channel 440 is provided in face 44!, in which channel is slidably mounted a dog member 41 provided with an axially extending tooth "it which also extends radially towards the toothed periphery of and the reset functions. When sequential code signal-elements are utilized, as may be assumed inftheinstant'application, print magnet 54 is I controlledby the stop element of the permutaratchet gear 33. A member 44d, integral with member 44, extends axially into the channel 440, as shown in Fig. 5 and also part way diametrical- 1y of member 44. A spring member, as disclosed in saidPatent No. 2,206,646, abuts member 4411 and spring biases member 41 so that the tooth 4' tends to engage the teeth of ratchet gear 33. A dog lift lever 43 (see also Fig. 4) is pivoted by its ball-shaped end 48p fitted into a socket in the face 441, and extends crosswise of dog 41 and engages dog 41 with its center portion. The other end of lever 48 is cut diagonally to form a tooth 48t projecting beyond the circumference of member 44. A slot 448 is formed in the face of member 44, generally, at right angles to channel 440, to'permit oscillation of dog lift lever 48 with respect to 44, about the ball and socket connection, when 4813 is engaged by a stop member 49 controlled by the permutation disk members, as described later. This oscillatory movement of'lever 48 is transferred to dog 41 to move the dog, longitudinally of itself against the force of its biasing spring, and into the posi-.

tion as illustrated in Fig. 5. When a stop member 49 is moved radially to release tooth t, lever 48 will thereupon permit dog 41 to be moved to the left, as viewed in Fig. 5, under the tion ofcode elements of a full complete signal which complete signal when the 5-unit code is utilized comprises a start element, five code signal elements .proper, and a stop element.

Referringto Figs. 3 and '7, there is illustrated the permutation means associated with clutch 34 'for selectively. rotatively positioning the typewheel. As is seen in Fig. 3, clutch 34 is stopped by engagement of tooth 48f of its dog lift lever 48 with a tooth 49t of a stop member 49 (Fig. 5). Each stop member 49 is provided with a laterally projecting support member carrying its tooth 4% and also with a laterally extending support member carrying projection 49p (see also Fig. 4) which cooperates with notches in the permutative members, as described presently. The laterally extending support members for 49:. and 49p provide a channel 490. Eight such stop members 49 are distributed crcumferentially about clutch 34. A set of three permutation selector rings 56, 51, and 58 (Fig. 7) are disposed coaxially with clutch 34, the annular portion of the rings being located .within each of the channels 490 of the eight stop members, respectively. These rings aremaintained in position, coaxial with clutch 34, by-a projecting circular front portion 200 influence of its biasing spring, to thereby engage tooth 4'It and associated ratchet gear 33,

wherebythe rotation of gear 33 is transmitted to member--44 and shaft 44b.

Typewheel positioning Novel means are now provided for completely positioning the typewheel, which comprise means of casing 20- (Fig. 3) .andaby the eight stop members 49, distrib uted circumferentially of the permutation ring members. Each of the stops 9 v ismounted for'movenient radially of the annular permutation members and is constantly urged toward the center of the annular members by ,means: of an individual spring 49s. Each of the three permutation-rings is held against bodily lateral movement. by means, of a member 59 (see also Fig.6) prov ided" with an annular channel 596 inl whioh the rings are located. Member nected to its corresponding permutation ring (ring- 56, for example) whereby the ring is m tated clockwise upon counterclockwise rotation of lever 6|. Each lever BI is maintained in the cocked position, as illustrated in Fig. 3, by a, trigger element 62, pivoted at 62p and biased by spring 623 for clockwise rotation. A lug 62a. on

, trigger 62 engages a shoulder 810 on lever 6! to hold the lever 6| in cocked position. A link 63 is pivotally attached to each trigger 62 and is also pivotally connected to a pivoted armature 54, one for each of the magnets 50, and 52. respectively, (Fig. 3) and likewise one for each of the magnets 53, 54 and 55 (Fig. 4). Upon energization of any magnet, its associated armature G is rotated clockwise (as viewed in Fig. 3) to move the link 63 to the left, to rotate trig er 62 counterclockwise, to thereby release the cocked lever SI for counterclockwise rotation under the influence of its spring Sis, Whichilll nshes the motive power to in turn rotate the actuate the magnets and thereby the rings, since the work required to rotate the rings is actually performed by the springs Sis, the magnets merely controlling the trigger elements.

The relative rotation of the r ngs, 56, 58 and 5 aligns a single set of individual notches 55 (Fig. 4) formed in the outer peripheries of the respective rings. Since each ring can be operated to any one of two positions and since there are three rings provided, a total of eight permutative positions may be obtained. Each of the three rings (Fig. 7) is therefore provided with eight notches (as compared to the four notches as illustrated in Fig. 4) the notches on the respective rings being so positioned relatively to each other that a plurality of three notches, and three only; one only on each of the rings respectively; will be aligned for each of the eight rotative positions of the three rings, and such alignment occurs directly beneath one only, of the resiliently biased stops d9 cooperating with these three rings. The projection 89p of the particular stop, thus selected, will enter the three aligned notches of the three rings, respectively, while any previously aligned stop will be cammed out of its cooperating notches, and all of the stops, except the one now aligned, are held in their most remote radial position by the outer peripheries of the three rings.

A different stop is, therefore, permitted to move radially inward for each of the eight permutation positions of the three rings.

Furthermore the notches on the respective rings are so arranged, that clutch 34 will be rotated to any one of its several assumed positions, in the least possible time. For example, it may be assumed, as stated above, that under ordinary sequential code signalelement operation, magnets 50, 5| and 52 (Fig. 3) are energized by the first, second and fifth actual code signal ele- 20 -(Fig. 2).

ments, respectively, of a live element code. Upon energization of magnet 52, ring 58 will be released and that stop member 48, now illustrated in Fig. 3 as engaging dog lift lever 48, will be 5 cammed out of its associated notches 65, by point lap riding up the sides oi. the notches as the rin 58 is rotated clockwise, and dog lift lever 48 will therefore be released. The notches of the three rings 55, 51 and 58 are so chosen and arranged,

10 that when magnet 52 only is energized, and ring 58 only is rotated, the immediately adjacent stop, in a counterclockwise direction from the stopnow illustrated as engaging lever 48 in Fig. 3, will be aligned with three notches in the respective rings 55, 51 and 58. Therefore, when dog lift lever 48 is released from the position as shown in Fig. 3, dog 41 (Fig. 5) of clutch 34 is moved by its spring to engage tooth Mt and the associated rotating ratchet gear 30 of clutch 34 Clutch 34 is thereupon rotated until dog lift lever 58 (Fig. 3) engages tooth 5st of the immediately adjacent stop t9, and the clutch is thereby stopped after having completed oneeighth of a revolution. If magnet 5i only is energized, ring 51 only is released for rotation and clutch 35 will rotate one-quarter of a revolu tion from the position as shown in Fig. 3. If magnet 5| is first energized and magnet 52 is sequentially energized, the. clutch will be permitted to rotate three-eighths of a revolution.

If magnet 50 alone is energized, the clutch will be permitted to rotate a full half revolution. If magnets 50 and 52 are both energized, the clutch will be permitted to rotate five-eighths of a revolution, if magnets 50-and 5! are both energized the clutch will be permitted to rotate six-eighths of a revolution and if magnets 5B, 5! and 52 are all sequently energized, the clutch will be permitted to rotate seven-eighths of a revolution.

It is seen, therefore, that upon sequential operation of the magnets 50, 5| and 52, the clutch 34 will always advance to its selected position in the shortest possible time. This islikewise true of magnets 53 and 55 and their associated clutch 3? (Fig. 4). v

Novel means are also provided whereby all oi?v the levers 6| associated with magnets 50, 5|, 52, 55. and 55 are resetto cocked position, as illustrated in Fig, 3, following the reception of each group of code signal elements comprising one complete signal, and lever Gib, associated with print magnet 55, is also reset. Upon release of the single revolution clutch #32 (Fig. 2), as described presently, shaft 43 is allowed to rotate one single complete revolution. During the rotation of shaft 53, a reset cam 56 (Figs. 2 and 3) carried by shaft 63 for rotation therewith is engaged by a roller ti on reset lever 58 (Fig. 3) which roller is continuaily biased against the 0 cam 66 by means of spring 68s acting on lever 58.

Upon this rotation of cam 66, the reset lever is rotated clockwise, as viewed in Fig. 3, and a lug .581) integral with reset lever 68 engages the sides of notches Gin formed in each of the three levers 6| (Fig. 3) to rotate these levers clockwise about their pivots against the force of their respective springs dis until the levers are restored to cocked position and locked by the triggers 62, as illustrated in Fig. 3. Levers GI and Gib (Fig. 4)

70 associated with magnets 53, 54 and 55 are si'mi-' I ,larly reset by cam 66a, roller 61a and lever'58a with its lug 58c. Continued rotation of cam 56 ,permits the lever 68 to rotate to the position, as shown in Fig. 3, so that rings 56,51 and 58 are free to rotate when the triggers 82 are released and levers 6| are operated. Restoration of the rings a ain aligns that particular stop 46, as illustrat d in Fig. 3, to permit clutch 34 to rotate until dog lift lever 48 engages the tooth 49t of stop 49, in the position as illustrated. It is to be noted'that theclutch 34 during this last portion of its movement, moves counterclockwise or in the same direction as during its previous operation, so that the restoration of the clutch 34 and its controlled shaft 35, which determines the rotative position of the type wheel 36, is always in the same direction. It is seen, therefore, that the clutch 34 can assume any one of eight rotative positions, determined by the permutations of code signal elements received, and is returned to a chosen normal position after reception of each complete code signal. Similarly clutch 31 can assume any one of four positions, and is returned to a chosen normal position while clutch 42 is limited to one complete revolution.

As illustrated in Fig. 5, each clutch is provided with a shaft 44b integral with the clutch body 44. Shaft 44b of clutch 34-(Fig. 1) is inserted in an axial opening in the shaft 35 and is connected to the shaft for rotation thereof by a pin 35p. Upon rotation, therefore, of clutch 34, to any one of its eight positions, this rotation is transmitted to shaft 35. f. 7

A lower end of shaft 35 is reduced in diameter and passes through bracket 69 attached to the front panel 26a and also passes through an axially extending bored portion 69a integral with bracket 69 and into an axial opening 36a formed in the cylindrical cam 38 whereby the cam 38 is aligned with shaft 35. A spring 36s surrounds the upper end of shaft 35 and resiliently biases the typewheel 36 downwardly, as

viewed in Fig. 1. Shaft '35 is provided adjacent its reduced portion with a pair of axially extending key ways 35k, 35k. A groove collar member ID (see also Fig. 9) is provided with radially inwardly extending lugs extending into the key.ways 35k, respectively, whereby the rotation of the shaft 35 is transmitted. to member ID, but with member I6 free to move axially of shaft 35. Integral with collar 10 is a disk-16d provided with opposite, radially extending slots Ills, Ills (Fig. 9). A cylindrical member 160, also integral with collar Ill, extends axially of and surrounds the shaft 35 (Figs. 1 and 9). A circumferentially extending groove 169 (Fig. 9) formed in the end of member 160 provides a'bearing race for the ball bearings 36b (Fig. 1) which also engage a race formed in the interior of typewheel 36, to provide an antifriction mounting for the typewheel, so that the typewheel can be with an axially extending opening in which is, inserted a spring II and a retaining ball I2.-

The end of the axially extending opening in typewheel 36 is smaller than the diameter of the ball so that only aportion of a hemisphere of ball 12' extends externally of the bottom face of typewheel 36 (Fig. 1). A radially slidable, zone selection or shift member I3 (Fig. 9) is mounted on cylindrical member 160 by means of an elongated or elliptical opening 13a formed in the slide I3. Slide I3 is provided on one face with a pair of projecting lugs 'I3bl, 13b2, disposed on opposite sides diametrically of slide I3, which lugs fit into and abut the sides of slots 16s when member I3 is mounted in position on member 100, as illustrated in Figs. 1, 2 and 10. The opposite face of slide 13 is provided with a cylindrical operating lug 130 which rides in and engages the sides of slot-I4 (Figs. 9 and 10) Upon radial movement of slide I3 in such a direction that operating lug 130 is moved radially inward,

the lug engaging the sides of groove I4 will rotate the typewheel 36 one-sixteenth of a revolution in one direction, while upon movement of slide I3 radially, in such a direction that lug 13c moves radially outward, the typewheel 36 is rotated in the opposite direction one-sixteenth of a revolution.- A single lug 130 only, cooperates with a single radial groove I4 only, and serves to rotate the typewheel in either one of two required directions. A pair of indentations 13c, lie, is provided on the same face of slide I3 as operating lug 13c (Fig. 9) adjacent the typewheel 36. Up-

on radial movement of slide I3 in one direction,

- Figures and Letters characters.

ball I2 engages one indentation, and upon radial movement in the opposite direction, ball I2 engages the other indentation, to thereby retain slide I3 in either of its assumed positions. Ball I2 and the indentations I3e..also serve to retain the typewheel 36 in one or the other of its rotative positions with respect to shaft 35. An abutting mg 131), for cooperation with shift operating mechanism, to be described presently, is also provided on this same face.

As is seen in Fig. 2, typewheel 36 is provided with sixteen vertically extending columns of characters, each column comprising alternately By rotation of the typewheel 36 under control of shaft 35 and clutch 34, any one of eight uniformly, circumferentially distributed columns of characters is selected, and upon further rotation of the typewheel one-sixteenth of a revolution, with respect to shaft 35, one of two adjacent columns of characters, namely Figures or Letters, is chosen, so that the final rotative positioning of the typewheel with respect to shaft 35 is a zoning or shift function. This zoning or shift function will be described in detail presently, and is produced by engagement of shift operating mechanism with the abutting lug 13b (Fig. 9) or the lug I3bl, which last lug serves the dual purpose of an abutting and a guiding lug.

Novel means for axially positioning the typewheel will now be described. 6

Axial positioning of typewheel The two magnets 53 and 55 (Fig. 4) and the associated permutation ring members I5 and I6, which are similar to the ring'members 56, 51 and 58, described above, control mechanism which in turn controls the axial positioning of the typewheel. Magnets 53 and 55, respectively, control the rings I5 and I6 by means of armatures 64, links 63, triggers 62 and pivoted levers (ii, in the same manner as magnets 59, 5t and 52 control their respective rings 56, 5'! and 58. Relative rotation of rings I5 and I6 selectively aligns their notches 65 in different permutations, so that the four steps 49 (Fig. 4), cooperating with rings I5 and I6, may be selectively rendered roller 61a, lever 88a and lug 880 in the same manner as the permutation disks 58, 51 and "are reset by means of theirassociated cam 86, roller tions.

Similarly, as is seen from Fig. 4, the magnet 56, which may be designated the print magnet, controls its trigger 62 by means of its associated armature 64 and link 63. Trigger 52 of the print magnet 54 controls a pivoted lever Bib, generally similar to the levers SI, and pivoted for rotation about pivot Biz). Lever Bib, however, is not attached to any permutation ring member but projects into the path of rotation of the dog lift lever 48-of clutch 42, and is held in position to intercept the lever is, by coaction with its trigger 82. Upon energization of print magnet 56, its trigger t2 releases lever ii lb for rotation clockwise under control of its associated spring 68s until the end of lever tlb is moved out of the path of rotation of lever 48, and the single revolution clutch 42 is released for rotation. Also, lever Bib is reset to the position, as indicated in Fig. 4, by means of the reset cam eta, roller 63c, reset arm 58a and lug 68c employed in resetting the permutation disks l and E5. The cam 86a (Fig. 2)

' sition, .as illustrated in Fig. 4, in time to intercept the dog lift member 48 and halt the lever (it in the position, as shown, to thereby terminate the single revolution of clutch 52. The shaft 4% (Fig. 5) of clutch 42 is inserted into an opening in the shaft 43 (Fig. 2) andis connected to the shaft 43 .by a pin connection (lac.

The shaft 641) of clutch 8i (Fi l) is inserted into the axial opening 38a of cylindrical cam member 38 (Fig. 1) and is attached to cam member 38 by pin 381) so that the rotation of, clutch 31 is delivered to the cam member 38 to rotatably position the cam member in any chosen one of four possible positions. Cam member 38 is provided with a cam groove 38g. Athick roller ll engages the sides of cam groove 389, as seen in Fig. 1, and means are provided whereby roller Ti is moved up and down, or axially of shaft 35,

upon rotation of cam member 38. A thick plate member 18 is attached by screws is to the front panel 2041. Cut into the edge of plate 19, adiacent the cam element 38, is alarge groove 18g! (Fig. 2). In the opposing side walls of groove I8gl there are also out two pairs of small guide grooves 1892, the respective grooves of each pair being aligned in the direction of the thickness of plate 18. A plurality of thin rollers 80, of slightly larger diameter than roller H, is carried by a member 8| and theserollers ride in the groove 'I8g2, to provide an antifriction mounting for the member 8| and to retain it within the large groove 18g! of plate 18. Roller" is also attached to member 8| and upon rotation of the cam member 18, since the roller H is restrained, by means of member 8|, against bodily rotation with member 3B,the roller H is moved upwardly or downwardly as it rides upon the sides of cam groove 38a. The upward and downward motion of roller 11 is transmitted tomember 8|,

which also carries a second roller 'I'Ia, similar to roller 11, adjacent its upper end (Fig. 1). Roller 11a is located within the groove m of the grooved collar 10, which collar, a 'stated above, is

"mounted for rotation with shaft 35 but is free to move axially thereof. Roller Tia transmits the axial movement of roller H and member 8| to the collar 10. Since, as described above, the collar I0 is integral with disk 10d (see also Fig. 9) while 10d and slide l3 carry the typewheel 36, the typewheel is selectively positioned axially, in any one of four chosen axial positions upon rotation of cam member 38 and consequent axial movement of member 8i. typewheel 36 is provided with four horizontal rows of characters extending circumferentially about the periphery of the typewheel so that any one row can be chosen by the axial positioning of typewheel 36. By the rotative positioning of the typewheel under controlof clutch 3%, as described above, any one of eight circumferentially, uniformly distributed vertical columns of characters can be selected. It is therefore seen, that by the combined axial and rotative movement of typewheel 3%, any one character, out of any one of eight vertical columns of characters, can be selectively located in position for printing. In order, however, to select one of two characters-out of one of two adjacent vertical columns, novel shift or zone positioning mechanism is provided,

which will now be described. 4

Zone positioning or shift Novel means are now provided cooperating with novel means on the typewheel, as shown and described in applicants copending application Serial No. 419,575 filed November 18, 1941, which matured into Patent No. 2,307,123, January 5, 1943, for producing zone positioning or shift. In

one extreme axial position of the typewheel, the I zone positioningor shift slide element i3 is so 7 located axially and also oriented circumferentially that the shift operating mechanism can radially shift slide 73 to rotate the typewheel one-sixteenth of a revolution in one direction, which operation comprises one shift function of the typewheel from"Letters to Figures or vice versa. In the other extreme axial position of the typewheel, slide 13 is so located axially and also circumferentially that the shift operating mechanism can rotate the typewheel one-sixteenth of a revolution, in the opposite direction, which' comprises the other shift function.

. As described above, slide i3 is mounted for radial movement by means of the lugs 13b! and HM (Fig. 9) cooperating withslots Ills in member lfldAsin'gle operating lug is also provided, as described above, cooperating with the sides of the generally radial slot 14 in the typewheel 38 to rotate the typewheel one-sixteenth teenth of a revolution in the opposite direction.

As shown in Figs. 2 and 10, a pair of shift operating levers 82 and 83 is provided. When standard teletype shift signals are employed, the "Figures signal places the typewheel 36 in its extreme lower position, as viewed in Fig. 2, while As is seen from Fig. 2,

When the shift operating mechathe Letters shiftsignal places the typewheel 36 in its extreme upper position. Lever 92 cooperates with lug l3bl, in the extreme lower position of typewheel 36, to radially move slide 13 so that lug 130 is moved radiallyinward to rotate typewheel. 36 and perform the Figures" shift function. Lever 83, on the other hand, cooperates with abutting lug 13b, in the extreme upper position of typewheel 35, to move lug 73c radially outward and thus rotate typewheel 36 to perform the Letters shift function.

As is seen in Fig. 10, levers 82 and 83 are eachpivotally mounted for oscillation about pivots 82p and 8317, respectively.

An elongated slot 83s is formed in lever 83. Spring 84, attached at one end to a lug 85 firmly fixed to the frame 20, is hooked at its otherend to lever 83 and urges lever 83 to the position, as shown in Fig. 10, with the pivot 83p engaging the wall at one end of slot 83s. If, for any reason, lever 83 is prevented from rotating about pivot 83p upon operation of its operating cam, as described presently, lever 83 and slot 83s are moved to the right, as viewed in Fig. 10, and against the force of spring 84 whereby breakage of the lever 83 is prevented. Lever 82 is similarly resiliently mounted on pivot 8217. Further, levers 82 and 83 are respectively mounted for movement axially of pivots 82p and 83p, respectively, and against the force of associated springs 82a. and 83a (Fi 2) so that the levers 92 and 83 are further protected against breakage due to strain.

Each of the levers 82 and 83 is provided with an operating lug 82b and 83b, respectively (Fig. A cam 86 (Figs. 2 and 10), mounted on shaft 43 for rotation therewith, is provided with a pair of oppositely extending cam rollers 89a and 36b, cooperating respectively with lugs 82b and 83b of the shift operating levers 82 and 83. As shaft asaasse A13 is rotated, cam 9t rotates its cam rollers 89a and 86b to simultaneously engage the lugs 92b and 83b, respectively, to simultaneously oscillate levers 82 and 83 about their respective pivots.

Upon reception-of the Figures shift signal,

the typewheel is positioned in its extreme lower position,,so that upon oscillation of lever 82, its

operating end 820 will engage lug 1317! (Fig. 9) of slide 73 to radially move this element and thereby rotate typewheel 36 one-sixteenth of a revolution in one direction, as described above, to perform the Figures shift function. On the other hand, upon reception of the Letters shift Tape feed Novel tape feeding and tape guiding mechanism, as shown and described in applicants" copending application Serial No. 419,576, filed November 18, 1941, which matured into Patent No.

2,307,123, January 5, 1943, is provided for feeding the tape; step by step, past the printing position and for guiding the tape. A rol1 of tape 81 (Fig. 3) is mounted within the tape roll support 88 attached to frame 20 by a bolt 88a and slotted link 88b. Tape 81 unwinds from its roll and I passes under a guide roller 89 to a printing hammer support member 90 and within the upper tape guide slot 90a (Fig. 10), beneath a novel arcuate-shaped tape guiding member, described presently, and aro nd the end 991) of the hammer support 90, d into lower guide slot a and tapeguide 9| (see also Fig. 1), across the front panel 20a of the printer, so that as the characters are printed' by the printing mecha nism, the printed characters appear immediately in easily readable position on' the face of the printer. Tape 81 (Fig. 3) is then fedbetween the knurled feed rollers of the novel tapefeeding mechanism, which will now be described.

Mounted on shaft 43 for rotation therewith is an eccentric disk cam 92 (Figs. 2 and 3) provided with a peripheral and radially extending slot 93 (Fig. 2). An unequal Y-arm lever 93 pivoted at 94p is provided with a short arm a shaft 91 journaled in member 98 attached to the front panel 2nd. by pivot 98p. A series of holes 967) are provided in lever 95 whereby the connection of link 95 to lever 95 can be varied, to change the amount that the tape is fed for each oscillation of lever 99. In this manner, the spacing of the characters on the tape can be varied at will- Lever as, upon oscillation in a counterclockwise direction, similarly oscillates eccentric 95a. Balls 99 located between the outer periphery of member ttannd an inner race Hill of gear lfll, mounted freely on shaft 21, lock the member Sta and race 8% together upon such counterclockwise rotation, due to the eccentricity of the periphery of member 96a. Balls "it are constantly urged towards engaging position by the spring elements Nita abutting the straight ledge portion of the fingers, respectively, of member 96a. Upon the return stroke; in a clockwise direction, of lever 96, the balls 50!? no longer wedge together eccentric member 960, and the race it!) of gear iti, and gear lei will not rollers 193 (only one shown in Fig. 3) engaging the tape 3?. -Gear H02 meshes with gear are, suitably mounted for rotation on panel 200., and carrying another pair of knurled rollers I05 (only one shown) aligned respectively with the knurled rollers its, so that the feed rolls are rotated to feed the tape past the printing position, the amount of tape feed, and the spacing of the characters on the tape, being determined by the particular connection between link 95 and lever 96, as described above. The tape 81 can also be pulled by hand to feed the tape past the printing position, since this action rotates gear iili counterclockwise, so that the balls 99 do not lock with eccentric member 96a.

Frame 98 is pivoted at 9827, as stated above, and is urged constantly counterclockwise by spring 988 so that the respective knurled :feed rollers I03 are held tightly in engagement with the tape 81 and force the tape 81 tightly into engagement with the respective rollers I05. To

feed a new tape, frame 98 can be forced clockasoasee wise, against the force of spring 98:, to release the pressure between the buried rollers I03 and I053.

As is seen from Fig. 10, the end 901) of the 9% at one end and to member It? at th other.v

end to bias the tape guide member "it to the position, as shown in Fig; 10. When a tape is inserted into the upper tape guide slot the and fed to the right, by hand, memher'lola is urged manually to the left, to rotate the arcu= ate member tilt clockwise to a position between the end 9% of member so and thetypewheel 3E. The arcuate member thereby serves as a guide to thread the tape around the sharp bend of end he?) or" member and into the lower guide slot the of member stand the tape guide 92 on the front panel of the printer. Member iiiia is thereupon released and assumes the position, as shown in Fig. 1c, and tape a? (Fig. 3) is fed by hand between the knurled rollers tilt and its, by clockwise rotation of frameeli. as described above. The tapeis then ready for automatic feed under control of the tape feed mechanism as controlled inturn by the rotation of shaft Ribbon feed and ribbon reversal mechanism 558 (Fig. 3) is provided, which may be of the type as shown and described in applicants co pending application Serial No. 35%,935, filed August as, 1940, to which reference may be had for a more detailed description. The ribbon reed mechanism is operated by link its (Fig. 3) corn nected to the long arm eat of the unequal f-- Printing mechanism Novel printing and printing control mechanism is provided, as will now be described. A reciprocable hammer member 552 (Figs. 10 and ll), provided with a printing head Mia, is mounted for reciprocation printing hammer support member 99. A threaded member lit (Fig. 10) threaded into support til provides an interiorly locatedabutting surface i its against which rests one end of a coil spring His! surrounding the hammer i and abutting the lugs M22), M22}, integral with hammer H2 and urging hammer head i ifia to engage the tape 8?, ribbon Hi3 and typewheel 36. A pair of opposed shoulders H20 and 2d (Fig. i1) is also provided on hammer H2. Aspring 832s? (Fig. 1G) surrounds hammer H2 and rides freely between shoulders i We and i l2d, in the cooked position of hammer M2, as illustrated in Fig. 16, and the coiled spring extends above and below the fiat top and bottom surfaces of hammer head ii2a (Fig. 100;). Upon release of the hammer from its cocked position, shoulder H20 moves spring H252 into engagement with a shoulder the (Fig. 101?.) of member so, and the spring i list is compressed as hammer head lite impinges against tape ill to engage the tape, ribbon ill? and typewheel 38.

The compressed spring H233 thereupon exerts its force against oulder 2c and moves the released hammer ou of engagement with the tape, to thereby release the tape, ribbon and typewheel.

Hammer M2 is also provided with a latching shoulder H22 (Figs. 10 and 11) which engages a tooth tilt of a trigger lever Hi3 pivoted at Hflp. Trigger lid is biased inv a counterclockwise direction by a spring lids. A cylindrical lug do. is provided on trigger lid for releasing the trigger. Bell-crank H5 (Fig. 10) ispivoted at: H59

and is biased in a counterclockwise direction by spring l its. The 'bell-crafikilt is provided at one end of one'arm thereof with an operating lug to which is engaged bycam roller Moo of cam lit mounted'for rotation with shaft is, and at the end of its other arm, bell-crank H5 is pro.- vided with a triggering lug filth located beneath the cylindrical lug lids (Fig. 10) of trigger i'il (see also Fig. 11). Upon rotation of shaft 63,

com H6 is rotated to engage cam roller iita and operating lug tide of bell-crank M5, to oscillate the bell-crank lit clockwise against the tension of spring tits, whereby triggering lug filth engages lug ti le to oscillate trig er M l clockwise against the force of spring lids so that tooth 5 Hit of trigger lid and shoulder ilZe of hammer Hi2,

are released, to release the hammer for move bell-crank H8 is provided with an operating lug iliib (Fig. ll) cooperating with one lug H271 oihammer M2. Bell-crank lit; is spring-biased in a counterclockwise direction in the same man her as hell crank ltd. As shaft 33 rotates, cam ill, in engagement with-roller Mild, oscillates bell-crank iii? clockwise to engage lug iitb of its lower arm with. a lug filth of the hammer M2 whereby the hammer is shifted to the left (Fig. 10) against the force of spring ii 2st, to compress this spring and cock the hammer. When the hammer is cocked, it assumes the position, as illustrated in Fig. 10, with lug iiZe of the hammer engaging tooth iidt of trigger lid and the trigger iiii therefore holds the hammer in cocked position until trigger lid is oscillated clockwise by bell-crank lit, as described above, to release.

hammer i it to perform its printing function.

Novel means are also provided for adjusting the degree of efiectivenes's of the printing hammer during the printing function which determines the clearance between the hammer head tile and the typewheel 36 when the hammer is released from its cocked position for impact against the tape to compress the tape and ribbon against the typewheel it. A micrometer screw HQ (Fig. 3) passes through a hole in the enlarged end 626a of lever lid and is engaged by a cooperating nut iida. By adjusting the screw lit, the lever 1126 can be oscillated about-its pivot 82hr) (Fig. 10) so that a stop lug 82% (Fig. 11) of lever i2ii can be adjusted in position between a lug l @222 of haer H2 and. the hammer head l 524:. As lug MB?) is moved to the left, as viewed in Fig. 11, the degree of eiiectivenessor the intensity of impact ofthe hammer head M211, is decreased, but as the position of lug 52% is adjusted to the right, as viewed in Fig. 11, the hammer head I l2a is permitted to approach closer to typewheel 36, when hammer H2 is triggered, and the degree of efiectiveness or of impact of the hammer H2 is increased.

General operation While the operations of the various elements of the completeprinter have been described in' connection with the individual elements, a brief description of the operation of all elements of the.

device will now be presented in order to clarify the coaction of the relative parts in producing printing of characters upon a tape in response to code signal permutations received, each permutation being representative of a character to be printed or a function tobe performed.

tape and typewheel, to the other spool and is ready for its automatic feeding operation.

Upon energization of the motor 2| (Fig. 3) .the respective ratchet gears 20 and 33 (Figs. 1 and 2) of the clutches 34 and 31 are rotated at 1200 R. P. M. and ratchet gear 4| (Fig. 2) of clutch 42 is rotated at 900 R. P. M.

Upon reception of a complete signal, comprising a start element, five signal elements of the signal proper, and a stop element, well known start-stop mechanism is released for rotation in synchronism with the received code signal elemerits so that the five signal elements of the signal proper, or any permutations thereof, are provided at the receiver, in accordance with the permutations of signal elements received.

Upon reception of the five signal elements, comprising a code signal permutation proper, certain of the magnets 50, and 52 (Fig. 3), 53 and 55 (Fig. 4) will be energized. Upon energization of any one of the magnets 52, 5| or 52, the permutation rings 56, 5'! and 58 (Fig. 7) will be released by the triggers 62 (Fig. 3) for relative rotation, to align certain of the notches 65 so that a chosen stop element 49 will be permitted to enter the aligned notches, and as the rings are operated to align these notches the stop element, previously aligned, will be cammed out of its notches and dog lift lever 48 will be released and clutch 3.4 will be engaged by engagement of tooth 41t (Fig. l) and the teeth of ratchet gear 30 which, as stated above, is rotated 1200 R. P. M. Shaft 35 will therefore be rotated until dog lift lever 48, (Fig. 3) engages the newly aligned stop 49 to thereby rotatively position the clutch 34, shaft 35, and typewheel 36, in accordance with the permutation of code signals controlling the magnets 50, 5! and 52. Similarly, magnets 53 ad 55 (Fig. 4) are energized selectively, by the received code signal permutation, and permutation rings 15 and 16 (Fig. 8) will be relatively rotatively positioned to permit entry of a stop element 49(Fig. 4) into the newly aligned notches 65, while the previously aligned stop element is cammed out of the notches and dog lift lever 48' is released for further rotation. The associated clutch 31 will be thereupon rotated until the newly selected stop is engaged by dog lift lever 48 and clutch 31 75 Of a rev lu i n to Produce the Figures shift will. rotate the cylindrical cam 33 (Fig. l) to rotatively position it in accordance with the particular permutation of code signal elements controlling magnets 53 and 55.

Rotation of cylindrical cam 38 will axially position the follower l1 and slidable element 8| to thereby similarly axially position the roller 11a and, grooved collar attached to the typewheel 36, to axially position the typewheel in one 10 of four axial positions, to select one of the four horizontal rings of characters (Fig. 2).

Since shaft 35 and typewheel 36 were rotatively positioned to choose one of sixteen unlformly spaced vertical columns of characters and since rotation of cylindrical cam 38 has axially positioned the typewheel to select one of the horizontal rings of characters, one character only will be selectively located in printing position and this character is that one repreg sented by the permutation of 5-code signal elements of the signal received.

Upon energization of magnet 54, which may be designated as the print. magnet, its associated clutch 42 (Figs. 2 and 4) will be released for one complete revolution, and since ratchet gear 4| (Fig. 2) which drives clutch 42, rotates at 900 13.. P. M., the shaft 43 rotated by clutch 42 will also rotate at this speed.

Since shaft which rotatively positions the u typewheel and since cylindrical cam. 38 which axially positions the typewheel are both driven at 1200 R. P. M. While shaft 43 is rotated at 900' R. P. M., regardless of which stop elements are selected, the shaft 35 and cylindrical cam 38 will always have completed their rotation and will be halted by the time the shaft 43 has completed three-quarters of a revolution. With the sequential system of signal transmission, as assumed in the instant application, the typewheel 40. will be completely positioned even quicker with respect to the rotation of shaft 43.

As shaft 43 rotates its one complete revolution, the cams attached thereto will be also rotated, in fixed time sequence. The ribbon H0 and 45 tape 81 will be advanced by rotation of disk cam The intensity of impact of the printing hammer is adjusted by screw H8 (Fig. 3) and the spacing of the characters on the tape is controlled by the particular hole 96b utilized in connecting link 85 to the tape feed lever 96. After printing has been performed, the cams 66 and 66a reset the permutation rings 56, 51, 58, i5 and 16 to the normal position, preparatory to reception of the next code signal permutation, and likewise the lever Bib (Fig. 4) controlled by the print magnet 54 will be reset to the position, as

indicated in Fig. 4, to engage the dog lift lever 48 and stop the single revolution clutch 42 at the end of its single revolution.

If the code signal permutation is received and is representative of the "Figures shift function,

the permutation rings will be so positioned that the cylindrical cam 38 will axially locate the typewheel in its extreme lower position and shaft 35 will so rotatively locate the typewheel that 7 lug 13b| of slide '13 will be engaged by the operating lug 820 of shift lever 82, when lever 82 is oscillated by roller 86a of cam 86 (Fig. 10) upon rotation of shaft 43. Slide 13 will thereby be shifted to rotate the typewheel 36 one-sixteenth function and the permutation rings will be subsequently reset to normal position and the lever Glb of the print magnet 54 to the position, as illustrated in Fig. 4, by operation of the reset arms 68 and 68a.

If the permutation code signal received is representative of the Letters shift function, the permutation rings will be so positioned that the typewheel 36 will be located in its extreme upper position and so positioned rotatively that lug 13b on slide 13 will be engaged by operating lug 830 of shift lever 83, upon rotation of shaft 43 and consequent rotation of am roller 86!) on cam 86, to rotate the typewheel one-sixteenth of a revolution to perform the Letters shift function. Subsequently, the permutation rings will be returned .to normal position and the lever 6lb of the print magnet 54 to the' position, as indicated in Fig. 4, by means of the reset levers 68 and 68a. In the two shift positions of the typewheel, there are no characters opposite the hammer H2 so that no character is printed upon the tape 81 during performance of the shift functions.

Novel printing mechanism, and novel mechanism for controlling the effectiveness of such printing mechanism are therefore provided.

While there has been shown and described and pointed out the fundamental novel features of the invention, as applied to a single embodiment, it will be understood that variousomissions and substitutions and changes in the form and details of the device illustrated and in its operation, may be made by those skilled in the art, without departing from the spirit of the invention. It is the intention, therefore, to be limited only as indicated by the scope of the following claims.

What is claimed is:

1. In a device of the character described, a typewheel, a printing hammer, means biasing said hammer toward said typewheel, and means for controlling the operation of said printing hammer comprising a rotatable cam, a bellcrank lever engageable with said cam at one end of said lever and with said hammer at the other end of said lever whereby upon rotation of said cam said bell-crank lever is oscillated to move said hammer against the force of said biasing means to thereby cock said hammer, latch means, means biasing said latch means towards said hammer, means on said latch means cooperating with means on said hammer to lock said hammer in cocked position, a second bell-crank lever, and cam means controlling said second bell-crank lever for moving said latch means against the force of its biasing means to release said hammer for printing opfor controlling the operation of said printing hammer comprising a rotatable cam, a bellcrank lever engageable'with said cam at one end of said lever and with said hammer at the other end of said lever whereby upon rotation of said cam, said bell-crank lever is oscillated to move "said hammer against the force of said biasing means to thereby cock said hammer, latch constantly engaging the hammer for biasing said hammer away from said typewheel to move said hammer away from said typewheel after the printing function is effected.

3. In a device of the character described, a typewheel, a printing hammer, means biasing said hammer toward said typewheel, means for cocking said hammer against the force of said biasing means, a pivoted member, means on said member engageable by means on said hammer upon release of said cocked hammer, and means for adiusting the rotative position of said pivoted member to thereby adjust the degree of effectiveness of said hammer upon said typewheel.

4. In a device of the character described, a typewheel, a printing hammer, means biasing said printing hammer toward said typewheel, means for cooking and releasing said printing hammer to produce a printing operation, and

- means for adjusting the degree of effectiveness of said printing operation comprising a bell-crank, means pivotally mounting said bell-crank at one end thereof, a threaded member on the other end of said bell-crank, means cooperating with I said threaded member to oscillate said bell-crank about its pivot, a member on said bell-crank exmer and said typewheel, upon said oscillation of said bell-crank.

CLYDE J. FITCH.

KURT R. SCHNEIDER. 

